CN103438177A

CN103438177A - Multi-cam self-adaptive multi-gear automatic transmission

Info

Publication number: CN103438177A
Application number: CN2013103891253A
Authority: CN
Inventors: 周黔; 郝允志; 薛荣生; 朱飞; 冉洋; 赵学渝; 陈康
Original assignee: Southwest University; Chongqing Academy of Science and Technology
Current assignee: Southwest University; Chongqing Academy of Science and Technology
Priority date: 2013-08-31
Filing date: 2013-08-31
Publication date: 2013-12-11
Anticipated expiration: 2033-08-31
Also published as: CN103438177B

Abstract

The invention discloses a multi-cam self-adaptive multi-gear automatic transmission. The transmission comprises a box body, a power input shaft, a power output shaft, a self-adaptive variable-speed high gear assembly, a first gear assembly and a self-adaptive variable-speed n-gear assembly, wherein the output revolving speed of the n-gear assembly is lower than that of the high gear assembly and higher than the first gear assembly, and the n-gear assembly comprises a second gear, a third gear......and an nth gear. The multi-cam self-adaptive multi-gear automatic transmission has all the advantages of an existing cam self-adaptive automatic transmission, and is of a multi-cam multi-gear structure, therefore, sensitivity in the gear shifting process is ensured, jerking and jam during gear shifting are eliminated, driving comfort is improved, furthermore, energy is saved and consumption is reduced; the dynamic property, economical efficiency, driving safety and driving comfort of a vehicle are greatly improved. In addition, by means of the power output shaft, cams and the cooperative relationships among the cams, a cone clutch is locked after separation, elimination of the transmission gaps among transmission components is facilitated, transmission precision and efficiency are improved, and drive energy is saved.

Description

Many cam self-adaptings multidrive

Technical field

The present invention relates to a kind of speed changer structure of motor-driven driving, particularly a kind of many cam self-adaptings multidrive.

Background technique

In prior art, automobile, motorcycle, electric bicycle are all directly to control closure or Current Control speed by speed-regulating handle or accelerator pedal basically, or adopt hand-control mechanical automatic automatic transmission mode to realize speed change.The operation of driver is depended in the operation of handle or accelerator pedal fully, usually can cause operation and garage's situation not to mate, and causes motor or motor fluctuation of service, motor stall phenomenon occurs.

Motor Vehicle is not in the situation that knowing running resistance by the driver, the speed change gear that only rule of thumb operation is controlled, have unavoidably following problem: 1. when startup, upward slope and heavy load, because running resistance increases, force motor or engine speed to descend in the work of inefficient district.2. owing to not having mechanical transmission to adjust moment of torsion and speed, can only promote the use of in plains region, can not meet under mountain area, hills and heavy load conditions and use, dwindle using scope; 3. driving wheel place installing space is little, has installed after motor or motor and has been difficult to hold automatic transmission and other new technology again; 4. do not possess adaptive function, can not automatically detect, revise and get rid of driver's error in operation; 5. change when unexpected in the speed of a motor vehicle, must cause motor or engine power and running resistance to be difficult to coupling.6. continuing, distance is short, grade ability is poor, and accommodation is little.

In order to overcome the above problems, the present inventor has invented a series of cam self-adapting automatic gear shifting device, utilize the running resistance driving cam, reach self shifter and, according to the purpose of running resistance Adaptive matching speed of a motor vehicle output torque, there is effect preferably; Although aforesaid cam self-adapting automatic gear shifting device has above-mentioned advantage, stability and high efficiency improve a lot than prior art, but the part component structural is comparatively complicated, and the speed changer volume is larger, particularly do not form the structure of many grades of transmissions, be not suitable for truck; Simultaneously, because drive path is longer, particularly slow shelves, affect transmission efficiency, and stability is still not ideal enough; And, by the cam clutch process, having bite, affect the smoothness of self shifter process; Although increase than prior art, according to structural analysis, still have room for improvement working life on working life.

Therefore, need to a kind of above-mentioned cam self-adapting automatic gear shifting device be improved, be applicable to all automobiles so that the automobile of load-carrying, not only can self adaption with the change in resistance of travelling, do not cut off in the situation of driving force and automatically carry out shift speed change, solve the little problem that can not meet the complex condition road occupation of moment of torsion-rotation speed change, stationarity is good, further increases work efficiency, and has better energy conservation and consumption reduction effects; Can also realize many shift automatic variable speeds according to running resistance, further reduce the pause and transition in rhythm or melody sense and save to drive energy consumption; Simultaneously, shift process is smooth and easy without bite, is quick on the draw, and saves driving source, reduces energy consumption, and further improves working life, is applicable to all motor vehicle and uses, and makes the car load situation more steady.

Summary of the invention

In view of this, the purpose of this invention is to provide a kind of many cam self-adaptings multidrive, be applicable to all automobiles so that the automobile of load-carrying, not only can self adaption with the change in resistance of travelling, do not cut off in the situation of driving force and automatically carry out shift speed change, solve the little problem that can not meet the complex condition road occupation of moment of torsion-rotation speed change, stationarity is good, further increases work efficiency, and has better energy conservation and consumption reduction effects; Can also realize many shift automatic variable speeds according to running resistance, further reduce the pause and transition in rhythm or melody sense and save to drive energy consumption; Simultaneously, shift process is smooth and easy without bite, is quick on the draw, and saves driving source, reduces energy consumption, and further improves working life, is applicable to all motor vehicle and uses, and makes the car load situation more steady.

Many cam self-adaptings multidrive of the present invention, comprise casing, power input shaft and pto＝power take-off, described power input shaft and pto＝power take-off are arranged at casing and are rotatably assorted with it, also comprise top gear assembly, one grade of assembly and output speed lower than the top gear assembly n shelves assembly higher than one grade of assembly, n shelves assembly is second gear, third gear ... with the n shelves;

The top gear assembly is high speed machine intelligent self-adaptive speed changing assembly a, comprises the axial external conical sleeve a of cirque body, the axial inner conical drogue a of cirque body and speed change elastic element a;

The axial inner conical drogue a of described cirque body coordinates with the power input shaft transmission, the axial inner conical drogue a of cirque body is provided with axial inner conical surface and is coated at the axial external conical sleeve a of cirque body, and the axial external conical sleeve a of cirque body is provided with the axial male cone (strobilus masculinus) matched with the axial inner conical surface of the axial inner conical drogue a of cirque body; The axial external conical sleeve a of cirque body is coated at pto＝power take-off and coordinates by the driving cam auxiliary driving with it;

Described one grade of assembly and n shelves assembly include the intermediate reduction gear driving mechanism with free wheel device, the axial inner conical drogue of cirque body coordinates with the power intake transmission of intermediate reduction gear driving mechanism, between the clutch end of intermediate reduction gear driving mechanism and the axial external conical sleeve a of cirque body, by the secondary group of cam a transmission, coordinates, the secondary a that organizes of described cam comprises at least one cam pair;

Speed change elastic element a applies the pretightening force of the inner conical surface laminating transmission that makes its male cone (strobilus masculinus) and the axial inner conical drogue a of cirque body to the axial external conical sleeve a of cirque body; During the fast gear of described pto＝power take-off output power, the life of described driving cam by-product is to the axial thrust load of the axial external conical sleeve a of cirque body, this axial thrust load and speed change elastic element a pretightening force opposite direction; During described pto＝power take-off output n shelves power, the secondary group of described driving cam pair and cam a produces the axial thrust load to the axial external conical sleeve a of cirque body, this axial thrust load and speed change elastic element a pretightening force opposite direction;

Free wheel device is divided into one grade of free wheel device and n shelves free wheel device; One grade of assembly also comprises one grade of transmission shaft, and described one grade of free wheel device outer ring coordinates with the axial inner conical drogue a of cirque body transmission, and one grade of free wheel device inner ring coordinates with transmission shaft driven, and one grade of transmission shaft coordinates with the secondary group of cam a transmission as one grade of clutch end;

In n shelves assembly, also comprise n shelves back shaft and n shelves mechanical intelligent adaptive rate assembly, n shelves back shaft is rotatably assorted and is supported in casing, and n shelves mechanical intelligent adaptive rate assembly comprises the axial external conical sleeve of n shelves cirque body, the axial inner conical drogue of n shelves cirque body and n shelves speed change elastic element; The axial inner conical drogue of n shelves cirque body is provided with axial inner conical surface and is coated at the axial external conical sleeve of n shelves cirque body, and the axial external conical sleeve of n shelves cirque body is provided with the axial male cone (strobilus masculinus) matched with the axial inner conical surface of the axial inner conical drogue of n shelves cirque body; The axial external conical sleeve of n shelves cirque body is coated at n shelves back shaft, and n shelves free wheel device outer ring coordinates with the axial inner conical drogue a of cirque body transmission, and n shelves free wheel device inner ring coordinates with the axial inner conical drogue transmission of n shelves cirque body; The axial external conical sleeve of n shelves cirque body exports n shelves power to the secondary group of cam a as n shelves clutch end by the secondary group of n shelves cam, the secondary group of this n shelves cam is when the transmission of n shelves, during described pto＝power take-off output n shelves power, the secondary group of described n shelves cam produces axial thrust load, this axial thrust load and the n shelves speed change elastic element pretightening force opposite direction to the axial external conical sleeve of n shelves cirque body.

Further, n shelves free wheel device inner ring also coordinates with the axial external conical sleeve of n shelves cirque body by n shelves locking cam is secondary, and the axial external conical sleeve of n shelves cirque body and this n shelves locking cam pair are rotatably assorted at circumferencial direction; N shelves locking cam pair applies axial thrust load to the axial external conical sleeve of n shelves cirque body, this axial thrust load and n shelves speed change elastic element pretightening force opposite direction;

Further, n shelves locking cam pair coordinates and forms by n shelves locking end face cam by between n shelves locking cam cover and n shelves free wheel device inner ring, axial contact and circumferencial direction is rotatably assorted between n shelves locking cam cover and the axial external conical sleeve of n shelves cirque body, the axial inner conical drogue of n shelves cirque body is provided with the axial inner conical drogue direct tube section of n shelves cirque body for coordinating with the transmission of n shelves free wheel device inner ring, described n shelves locking cam is placed in the axial inner conical drogue direct tube section of n shelves cirque body in overlapping and its cylindrical has annular spacing groove, at least one n shelves stop screw radially screws in the axial inner conical drogue direct tube section of n shelves cirque body and heads into annular spacing groove by the spacing ball of n shelves, the axial width of described annular spacing groove is greater than the spacing ball diameter of n shelves,

Further, n shelves back shaft is respectively second gear back shaft, third gear back shaft and fourth gear back shaft, and described one grade of transmission shaft, second gear back shaft, third gear back shaft and fourth gear back shaft are planetary structure and are centered around around pto＝power take-off, forms five speed transmission, second gear mechanical intelligent adaptive rate assembly, third gear mechanical intelligent adaptive rate assembly and fourth gear mechanical intelligent adaptive rate assembly correspondence respectively are arranged at second gear back shaft, third gear back shaft and fourth gear back shaft, one grade of transmission shaft is by one grade of driving gear and be placed in one grade of gear engagement pair that the first speed driven gear of pto＝power take-off forms and output power to the secondary group of cam a, the secondary group of second gear cam outputs power to the secondary group of cam a by the second gear driving gear be placed on the second gear back shaft with the intermediate gear engagement pair that the second gear driven gear be placed on pto＝power take-off forms, the secondary group of third gear cam outputs power to the secondary group of cam a by the third speed drive gear be placed on the third gear back shaft with the three-range transmission engagement pair that the third gear driven gear be placed on pto＝power take-off forms, the secondary group of fourth gear cam outputs power to the secondary group of cam a by the fourth gear driving gear be placed on the fourth gear back shaft with the fourth gear engagement pair that the fourth gear driven gear be placed on pto＝power take-off forms, the velocity ratio of described one grade of gear engagement pair, intermediate gear engagement pair, three-range transmission engagement pair and fourth gear engagement pair reduces successively,

Further, described first speed driven gear, the second gear driven gear, third gear driven gear and fourth gear driven gear are fixedly connected to form conjuncted driven gear, be placed in pto＝power take-off and be provided with at least two cam cover a, each cam cover a two ends is equipped with the end face impeller, between cam cover a, all by end face impeller engagement driving, form the secondary group of cam a between cam cover a and the axial external conical sleeve a of cirque body and between cam cover a and conjuncted driven gear, the shape line lift angle difference of the end face impeller at each cam cover a two ends, and the shape line lift angle of end face impeller that forms whole cams cover a of the secondary group of cam a is increased to the axial external conical sleeve a of cirque body gradually by conjuncted driven gear, be placed in n shelves back shaft and be provided with at least two n shelves cam covers, each n shelves cam cover two ends is equipped with the end face impeller, between n shelves cam cover, between n shelves cam cover and the axial external conical sleeve of n shelves cirque body and between n shelves cam cover and n shelves driving gear all by end face impeller engagement driving formation n shelves cam pair group, the shape line lift angle difference of the end face impeller at each n shelves cam cover two ends, and the end face impeller of whole n shelves cams covers of the secondary group of formation n shelves cam is increased gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body,

Further, free wheel device includes outer ring, inner ring and rolling element, be formed for the engagement space of with rolling element, meshing or separating between described outer ring and inner ring, also comprise the help roll assembly, described help roll assembly at least comprises and is parallel to free wheel device axis the help roll spaced with rolling element, described help roll cylindrical contacts with adjacent rolling element cylindrical, and described help roll arranges in the movable mode of the circumferencial direction at free wheel device;

Described help roll assembly also comprises the help roll support, described help roll with can along the free wheel device circumferencial direction slide and the mode of rotating around self axis by the help roll stent support between outer ring and inner ring;

Further, described help roll support comprises pushing out ring I and the pushing out ring II arranged corresponding to the help roll two ends, described pushing out ring I and pushing out ring II are respectively equipped with the circular groove along pushing out ring I and pushing out ring II circumferencial direction for penetrating for the help roll two ends, and described help roll two ends are slidably matched with corresponding circular groove; Described pushing out ring I and pushing out ring II are all between outer ring and inner ring, and the axial outside of pushing out ring I and pushing out ring II is respectively equipped with the radial bearing for outer ring and inner ring are rotatably assorted;

Further, described speed change elastic element a and n shelves speed change elastic element are speed change butterfly spring; Speed change elastic element a and n shelves speed change elastic element are respectively equipped with the pretightening force adjusting part, described pretightening force adjusting part comprises that axial limiting is installed on the adjustment disk of speed change butterfly spring end, described adjustment disk is provided with the end cam groove, and the end cam groove pushes against speed change dish spring by embedded adjustment pin;

Further, the pair of the driving cam between the axial external conical sleeve a of described cirque body and pto＝power take-off is the spiral prominence wheel set; The shape line lift angle that forms whole end face impellers of the secondary group of cam a increases to 60 ° by 24 ° by conjuncted driven gear gradually to the axial external conical sleeve a of cirque body; The shape line lift angle that forms whole end face impellers of the secondary group of n shelves cam increases to 60 ° by 24 ° gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body;

Further, the plane bearing that described speed change elastic element a and n shelves speed change elastic element all are coated at power input shaft by being slidably matched respectively and the plane bearing that is coated at n shelves back shaft that is slidably matched withstand the axial external conical sleeve a of cirque body and axial external conical sleeve one axial end portion of n shelves cirque body;

The diameter of described help roll be less than rolling element diameter 1/2nd; Described engagement space is by forming between the wedge slot of inner ring Excircle machining and inner ring cylindrical; Described radial bearing is rolling bearing, and pushing out ring I and pushing out ring II form respectively circumferentially inside axial ledge, and this axial ledge is withstood the interior ring of corresponding rolling bearing vertically;

Described n shelves free wheel device inner ring is rotatably assorted and is coated at n shelves cam cover cylindrical, and the n shelves locking end face cam of the axial external conical sleeve of n shelves cirque body is positioned on the step of its outer surface formation; The axial inner conical drogue a of cirque body is rotatably assorted and is coated at cam cover a and is provided with direct tube section, one grade of free wheel device outer ring and n shelves free wheel device outer ring are external toothing, the direct tube section of the axial inner conical drogue a of described cirque body is provided with the first driving gear with one grade of free wheel device outer ring engagement driving, with the second engaging gear of n shelves free wheel device outer ring engagement driving.

The invention has the beneficial effects as follows: many cam self-adaptings multidrive of the present invention, adopt the adaptive rate structure of many grades, all advantages with existing cam self-adapting automatic gear shifting device, if detect driving torque-rotating speed and running resistance-vehicle speed signal according to running resistance, make motor or engine output and traveling state of vehicle all the time in the optimum Match state, realize vehicle traction moment and the comprehensively balance control of running resistance, in the situation that do not cut off the driving force self adaption, with the change in resistance of travelling, automatically carry out shift speed change; Can meet under mountain area, hills and heavy load conditions and use, motor or engine load be changed mild, motor vehicle operate steadily, and improve Security; And adopt the structure of many grades, many cams, can guarantee the sensitivity in shift process, eliminate gearshift pause and transition in rhythm or melody sense and bite sense, improve ride comfort, further save energy and reduce the cost, greatly improve power character, Economy, drive safety and the travelling comfort of vehicle;

Simultaneously, utilize the matching relationship between pto＝power take-off, cam and cam in the present invention, the separation of locking conical clutch, simultaneously, also be beneficial to the drive gap of eliminating between transmission part, improve transmission accuracy and efficiency, save driving source, structural configuration is simply compact, and Transmitted chains is scientific and reasonable, and stationarity is good, and transmission shaft has stability of strutting system preferably, make the car load situation more steady, there is better energy conservation and consumption reduction effects, and reduce volume.

The accompanying drawing explanation

Below in conjunction with drawings and Examples, the invention will be further described.

Fig. 1 is that the present invention arranges schematic diagram;

Fig. 2 is that Fig. 1 is along A-A to cross-sectional view;

Fig. 3 is that Fig. 1 is along B-B to cross-sectional view;

Fig. 4 is the axial external conical sleeve a of cirque body and the axial external conical sleeve structure schematic diagram of n shelves cirque body;

Fig. 5 is cam cover a and n shelves cam nested structure schematic diagram;

The end cam that Fig. 6 is cam cover a and n shelves cam cover launches schematic diagram;

Fig. 7 is Fig. 2 C place enlarged view;

Fig. 8 is the overrun clutch structure schematic diagram;

Fig. 9 is Fig. 8 E place enlarged view;

Figure 10 is that Fig. 8 is along D-D to sectional view.

Embodiment

Fig. 1 is that the present invention arranges schematic diagram, Fig. 2 is that Fig. 1 is along A-A to cross-sectional view, Fig. 3 is that Fig. 1 is along B-B to cross-sectional view, Fig. 4 is the axial external conical sleeve a of cirque body and the axial external conical sleeve structure schematic diagram of n shelves cirque body, Fig. 5 is cam cover a and n shelves cam nested structure schematic diagram, the end cam that Fig. 6 is cam cover a and n shelves cam cover launches schematic diagram, Fig. 7 is Fig. 2 C place enlarged view, Fig. 8 is the overrun clutch structure schematic diagram, Fig. 9 is Fig. 8 E place enlarged view, Figure 10 is that Fig. 8 is along D-D to sectional view, as shown in the figure: many cam self-adaptings multidrive of the present invention, comprise casing 45, power input shaft 1 and pto＝power take-off 30, described power input shaft 1 and pto＝power take-off 30 are arranged at casing 45 and are rotatably assorted with it, as shown in the figure, power input shaft 1 and pto＝power take-off 30 coaxially arrange and all with casing, are rotatably assorted and form support, need be provided with necessary annular bearing with rolling contact, also comprise top gear assembly, one grade of assembly and output speed lower than the top gear assembly n shelves assembly higher than one grade of assembly, n shelves assembly is second gear, third gear ... with the n shelves, namely, between top gear assembly and one grade of assembly, also have n shelves, second gear, third gear etc., when n is four, have second gear third gear, fourth gear between top gear assembly and one grade of assembly, adds top gear assembly and one grade of assembly, forms five speed transmission,

The top gear assembly is high speed machine intelligent self-adaptive speed changing assembly a, comprises the axial external conical sleeve a13 of cirque body, the axial external conical sleeve a16 of cirque body and speed change elastic element a7;

The axial external conical sleeve a16 of described cirque body coordinates with power input shaft 1 transmission, the axial external conical sleeve a16 of cirque body is provided with axial inner conical surface and is coated at the axial external conical sleeve a13 of cirque body, and the axial external conical sleeve a13 of cirque body is provided with the axial male cone (strobilus masculinus) matched with the axial inner conical surface of the axial inner conical drogue a16 of cirque body; Coordinated transmission by the tapered sleeve structure, inner conical surface and male cone (strobilus masculinus) one of at least need have certain roughness, belong to that those skilled in the art can know according to this record, do not repeat them here; The axial external conical sleeve a13 of cirque body is coated at pto＝power take-off and coordinates by the driving cam auxiliary driving with it; The driving cam pair can be the spiral prominence wheel set or be processed into the end cam pair, all can realize the purpose of transmission;

Described one grade of assembly and n shelves assembly include the intermediate reduction gear driving mechanism with free wheel device, the axial inner conical drogue of cirque body coordinates with the power intake transmission of intermediate reduction gear driving mechanism, between the clutch end of intermediate reduction gear driving mechanism and the axial external conical sleeve a13 of cirque body, by the secondary group of cam a transmission, coordinates, the secondary a that organizes of described cam comprises at least one cam pair; Namely, the secondary group of cam a consists of cam pair transferring power successively, can be comparatively submissive for the clutch gearshift process, be specially adapted to many gear shift operations, and after gear shift, cooperatively interact and there is multi-locking function preferably with the driving cam pair, avoid the axial external conical sleeve a13 of cirque body play back and forth;

Speed change elastic element a7 applies the pretightening force of the inner conical surface laminating transmission that makes its male cone (strobilus masculinus) and the axial inner conical drogue a16 of cirque body to the axial external conical sleeve a13 of cirque body; During the fast gear of described pto＝power take-off output power, the life of described driving cam by-product is to the axial thrust load of the axial external conical sleeve a13 of cirque body, this axial thrust load and speed change elastic element a7 pretightening force opposite direction, the driving cam pair also applies axial force this responsive to axial force in speed change elastic element a to the axial external conical sleeve a13 of cirque body when carrying out transmission; During described pto＝power take-off output n shelves power, the secondary group of described driving cam pair and cam a produces the axial thrust load to the axial external conical sleeve a of cirque body, this axial thrust load and speed change elastic element pretightening force opposite direction, above-mentioned cam countershaft can be eliminated the matching gap of cam pair to component, effectively improves transmission accuracy;

Free wheel device is divided into one grade of free wheel device and n shelves free wheel device; One grade of assembly also comprises one grade of transmission shaft 61, described one grade of free wheel device outer ring 60 coordinates with the axial inner conical drogue a16 of cirque body transmission, one grade of free wheel device inner ring 59 coordinates with transmission shaft driven, and one grade of transmission shaft 61 coordinates with the secondary group of cam a transmission as one grade of clutch end;

In n shelves assembly, also comprise that (the present embodiment is five mark structures to n shelves back shaft, n shelves back shaft is divided into second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5) n shelves mechanical intelligent adaptive rate assembly (in five mark structures is, second gear shelves mechanical intelligent adaptive rate assembly, third gear mechanical intelligent adaptive rate assembly and fourth gear mechanical intelligent adaptive rate assembly) n shelves back shaft (second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5) being rotatably assorted is supported in casing 45, n shelves mechanical intelligent adaptive rate assembly comprises the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body), the axial inner conical drogue of n shelves cirque body (the axial inner conical drogue 50 of second gear cirque body, the axial inner conical drogue 37 of third gear cirque body and the axial inner conical drogue 10 of fourth gear cirque body) and n shelves speed change elastic element (second gear speed change elastic element 47, three class gear shift elastic element 41 and four-speed gear shift elastic element 6), the axial inner conical drogue of n shelves cirque body (the axial inner conical drogue 50 of second gear cirque body, the axial inner conical drogue 37 of third gear cirque body and the axial inner conical drogue 10 of fourth gear cirque body) be provided with axial inner conical surface and be coated at the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body), yes one to one, do not repeat them here, the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body) be provided with and the axial inner conical drogue of n shelves cirque body (the axial inner conical drogue 50 of second gear cirque body, the axial inner conical drogue 37 of third gear cirque body and the axial inner conical drogue 10 of fourth gear cirque body) the axial male cone (strobilus masculinus) that matches of axial inner conical surface, the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body) be coated at n shelves back shaft (second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5), n shelves free wheel device outer ring (as shown in the figure, second gear free wheel device outer ring 55, third gear free wheel device outer ring 33 and fourth gear free wheel device outer ring 18) with the axial inner conical drogue a16 of cirque body transmission, coordinate, n shelves free wheel device inner ring (as shown in the figure, second gear free wheel device inner ring 56, third gear free wheel device inner ring 34 and fourth gear free wheel device inner ring 20) and the axial inner conical drogue of n shelves cirque body (the axial inner conical drogue 50 of second gear cirque body, the axial inner conical drogue 37 of third gear cirque body and the axial inner conical drogue 10 of fourth gear cirque body) the transmission cooperation, the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body) by the secondary group of n shelves cam (the secondary group of second gear cam, the secondary group of third gear cam and the secondary group of fourth gear cam) export n shelves power to the secondary group of cam a as n shelves clutch end, the secondary group of this n shelves cam (the secondary group of second gear cam, the secondary group of third gear cam and the secondary group of fourth gear cam) when the transmission of n shelves, described pto＝power take-off 30 output n shelves (second gears, third gear and fourth gear) during power, the secondary group of described n shelves cam produces the axial thrust load to the axial external conical sleeve of n shelves cirque body, this axial thrust load and n shelves speed change elastic element pretightening force opposite direction.

In the present embodiment, n shelves free wheel device inner ring (second gear free wheel device inner ring 56, third gear free wheel device inner ring 34 and fourth gear free wheel device inner ring 20) also coordinates with the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body) by n shelves locking cam secondary (the second gear locking cam is secondary, third gear locking cam pair and fourth gear locking cam pair), and the axial external conical sleeve of n shelves cirque body and this n shelves locking cam pair are rotatably assorted at circumferencial direction; N shelves locking cam pair applies axial thrust load to the axial external conical sleeve of n shelves cirque body, this axial thrust load and n shelves speed change elastic element pretightening force opposite direction; While separating between the axial external conical sleeve of n shelves cirque body and the axial inner conical drogue of n shelves cirque body, the tractive force that utilizes n shelves free wheel device inner ring to produce is afterwards assisted locking to the axial external conical sleeve of n shelves cirque body in separation by axial thrust load, prevent its reciprocal clutch, guarantee the regularity and stability of gear shift.

In the present embodiment, secondary (the second gear locking cam pair of n shelves locking cam, third gear locking cam pair and fourth gear locking cam pair) by n shelves locking cam cover (second gear locking cam cover 51, third gear locking cam cover 39 and fourth gear locking cam cover 11) and n shelves free wheel device inner ring (second gear free wheel device inner ring 56, third gear free wheel device inner ring 34 and fourth gear free wheel device inner ring 20) between by n shelves locking end face cam (second gear locking end face cam, third gear locking end face cam and fourth gear locking end face cam) cooperation formation, n shelves locking cam cover (second gear locking cam cover 51, third gear locking cam cover 39 and fourth gear locking cam cover 11) and the axial external conical sleeve of n shelves cirque body (the axial external conical sleeve 48 of second gear cirque body, the axial external conical sleeve 40 of third gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body) between axially contact and circumferencial direction are rotatably assorted, the axial inner conical drogue of n shelves cirque body is provided with the axial inner conical drogue direct tube section of n shelves cirque body for coordinating with the transmission of n shelves free wheel device inner ring, described n shelves locking cam is placed in the axial inner conical drogue direct tube section of n shelves cirque body in overlapping and its cylindrical has annular spacing groove, at least one n shelves stop screw (as shown in the figure, the second gear stop screw, third gear stop screw and fourth gear stop screw) radially screw in the axial inner conical drogue direct tube section of n shelves cirque body and pass through the spacing ball of n shelves (the spacing ball 52 of the corresponding second gear of second gear stop screw, the corresponding spacing ball 38 of third gear of third gear stop screw and the spacing ball 12 of the corresponding fourth gear of fourth gear stop screw) head into annular spacing groove, the axial width of described annular spacing groove is greater than the spacing ball diameter of n shelves, during actual the use, a plurality of n shelves stop screws need along the circumferential direction be set, guarantee balance, n shelves locking cam cover is carried out to axial limiting, and the too much axial displacement of avoiding the n shelves locking end face cam by the tractive force input end to cause, realize stability preferably, as shown in the figure, be provided with ball between the axial external conical sleeve of n shelves cirque body and n shelves locking cam cover, to guarantee regularity and stability.

In the present embodiment, n shelves back shaft is respectively second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5, described one grade of transmission shaft 61, second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5 are planetary structure and are centered around around pto＝power take-off 30, form five speed transmission, as shown in the figure, one grade of transmission shaft 61, second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5 annular bearing with rolling contact by separately respectively are supported in casing 45 and are rotatably assorted with casing 45, certainly, n shelves free wheel device is also second gear free wheel device, third gear free wheel device and fourth gear free wheel device accordingly, n shelves mechanical intelligent adaptive rate assembly also corresponds to second gear mechanical intelligent adaptive rate assembly, third gear mechanical intelligent adaptive rate assembly and fourth gear mechanical intelligent adaptive rate assembly, and correspondence is arranged at second gear back shaft 46, third gear back shaft 44 and fourth gear back shaft 5 respectively, one grade of transmission shaft 61 is by one grade of driving gear 62 and be placed in one grade of gear engagement pair that the first speed driven gear 29 of pto＝power take-off 30 forms and output power to the secondary group of cam a, the secondary group of second gear cam outputs power to the secondary group of cam a by the second gear driving gear 58 be placed on second gear back shaft 46 with the intermediate gear engagement pair that the second gear driven gear 25 be placed on pto＝power take-off 30 forms, the secondary group of third gear cam outputs power to the secondary group of cam a by the third speed drive gear 31 be placed on third gear back shaft 44 with the three-range transmission engagement pair that the third gear driven gear 27 be placed on pto＝power take-off 30 forms, the secondary group of fourth gear cam outputs power to the secondary group of cam a by the fourth gear driving gear 24 be placed on fourth gear back shaft 5 with the fourth gear engagement pair that the fourth gear driven gear 28 be placed on pto＝power take-off 30 forms, the velocity ratio of described one grade of gear engagement pair, intermediate gear engagement pair, three-range transmission engagement pair and fourth gear engagement pair reduces successively, this layout makes the five speed transmission compact structure, and small volume reduces overall weight, is beneficial to the saving driving source, is applicable to the small trucks such as light card,

In the present embodiment, described first speed driven gear 29, second gear driven gear 25, third gear driven gear 27 and fourth gear driven gear 28 are fixedly connected to form conjuncted driven gear, and conjuncted driven gear can be integrally formed, can be also to be fixedly connected with by mechanical means; As shown in the figure, in the present embodiment, second gear driven gear 25, third gear driven gear 27 and fourth gear driven gear 28 are integrally formed, and 29 employing bolts of first speed driven gear are fixing to be connected with it, convenient processing; Be placed in pto＝power take-off and be provided with at least two cam cover a, each cam cover a two ends is equipped with the end face impeller, cam overlaps between a, cam overlaps between a and the axial external conical sleeve a13 of cirque body and cam overlaps between a and conjuncted driven gear all by the secondary a of group of end face impeller engagement driving formation cam, the shape line lift angle difference of the end face impeller at each cam cover a two ends, and the shape line lift angle of end face impeller that forms whole cams cover a of the secondary group of cam a is increased to the axial external conical sleeve a13 of cirque body gradually by conjuncted driven gear; As shown in the figure, cam cover a has three, is respectively cam cover a19,21,23; As shown in the figure, the cam of take cover a19 is example, the end face impeller 19a at its two ends and end face impeller 19b, the end face impeller 13b of the axial external conical sleeve a13 of cirque body, the end face impeller 26 of conjuncted driven gear, the mode that end face impeller 26 takes by mechanical connection is fixedly connected on conjuncted driven gear, convenient processing; The lift angle of the secondary a of group of cam adopts the structure increased gradually, is beneficial to and forms enough large axial thrust load and circumferential driving force, and can avoid bite; That is to say, for each cam cover a, little another lift angle of lift angle of end face impeller according to above-mentioned direction two ends is large, as shown in the figure, the end face impeller 19a lift angle α of cam cover a is less than end face impeller 19b lift angle β, the circumferential driving force of the assurance of lift angle β, and the assurance circumferential misalignment of lift angle α realize that sensitive axis to the axial external conical sleeve a13 of cirque body is to driving; Adopt the drive mechanism of multiterminal ground roll wheel, can guarantee the sensitivity in shift process, eliminate gearshift pause and transition in rhythm or melody sense and bite sense, drive a vehicle smooth and easy, improve ride comfort, further save energy and reduce the cost, greatly improve power character, Economy, drive safety and the travelling comfort of vehicle;

Being placed in n shelves back shaft is provided with at least two n shelves cam covers and (as shown in the figure, on the present embodiment second gear back shaft is three second

gear cams cover

53,54,57, on the third gear back shaft, be three third gear cam covers 36, 35, 32, on the fourth gear back shaft, be three fourth gear cam covers 14, 17, 22), each n shelves cam cover (second

gear cam cover

53, 54, 57, third

gear cam cover

36, 35, 32, fourth

gear cam cover

14, 17, 22) two ends are equipped with the end face impeller, n shelves cam cover (second

gear cam cover

53, 54, 57, third

gear cam cover

36, 35, 32, fourth

gear cam cover

14, 17, 22) between, all by end face impeller engagement driving, form the secondary group of n shelves cam between n shelves cam cover (matching with the axial external conical sleeve of n shelves cirque body) and the axial external conical sleeve of n shelves cirque body and between n shelves cam cover (matching with n shelves driving gear) and n shelves driving gear, each n shelves cam cover (second

gear cam cover

53, 54, 57, third

gear cam cover

36, 35, 32, fourth

gear cam cover

14, 17, 22) the shape line lift angle difference of the end face impeller at two ends, and the end face impeller of whole n shelves cams covers of the secondary group of formation n shelves cam is increased gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body, the effect produced is identical with cam cover a, all to be beneficial to form enough large axial thrust load and circumferential driving force, and can avoid bite, and adopt the drive mechanism of multiterminal ground roll wheel, can guarantee the sensitivity in shift process, eliminate gearshift pause and transition in rhythm or melody sense and bite sense, drive a vehicle smooth and easy, improve ride comfort, further save energy and reduce the cost, greatly improve power character, Economy, drive safety and the travelling comfort of vehicle, the structure of n shelves cam cover and cam overlap a19,21,23 similar, as shown in Figure 5, do not repeat them here.

When carrying out transmission, the secondary group of driving cam pair, secondary group of a of cam and n shelves cam plays the effect of common driving, and axial thrust load can be eliminated the matching gap between driving component, effectively improves transmission accuracy; Thereby, when not only can reaching slow shelves transmission, this structure separates preferably locking effect, also when transmission, improve quality of fit, reduce to coordinate surplus.

In the present embodiment, as Fig. 8, 9, shown in 10, because one grade of free wheel device is identical with n shelves overrun clutch structure, therefore, the fourth gear free wheel device of take describes as example: free wheel device includes outer ring 18, inner ring 20 and rolling element 65, be formed for the engagement space 63 of with rolling element 65, meshing or separating between described outer ring 18 and inner ring 20, also comprise the help roll assembly, described help roll assembly at least comprises and is parallel to free wheel device axis (be also the axis of inner ring 20 and outer ring 18) the help roll spaced with rolling element simultaneously, described help roll cylindrical contacts with adjacent rolling element cylindrical, described help roll arranges in the movable mode of the circumferencial direction at free wheel device (being also the circumferencial direction of inner ring 20 and outer ring 18) simultaneously, overrun clutch structure has herein comprised one grade of free wheel device and n shelves free wheel device, and structure is set forth no longer separately, this set-up mode has various structures, namely adopts existing mechanical structure, can realize that help roll gets final product the free wheel device circumferencial direction is servo-actuated, does not repeat them here, certainly, described help roll 66 diameters should be less than the distance between outer ring 18 inner circles and inner ring 20 cylindricals, make help roll 66 there is relatively freely radially activity space, avoid occurring the operation interference, thereby guarantee the smooth and easy operation of stablizing of rolling element 65 so that whole free wheel device.

Described help roll assembly also comprises the help roll support, described help roll 66 with can along the free wheel device circumferencial direction slide and the mode of rotating around self axis by the help roll stent support between outer ring 18 and inner ring 20; Guarantee rotation or the free sliding degree of help roll 66, thereby further guarantee the floating property of help roll 66, make between rolling element 65 and help roll 66 and form rolling friction when free wheel device moves, reduce power consumption, and make the stability of free wheel device better.

In the present embodiment, described help roll support comprises pushing out ring I 64 and the pushing out ring II 68 arranged corresponding to help roll 66 two ends, described pushing out ring I 64 and pushing out ring II 68 are respectively equipped with the circular groove along pushing out ring I 64 and pushing out ring II 68 circumferencial directions penetrated for confession help roll 66 two ends, and (Fig. 3 has expressed the circular groove 64a on pushing out ring I 64, circular groove 68a on pushing out ring II 68 and the circular groove 64a structure on pushing out ring I 64 are similar and all inside), described help roll 66 two ends are slidably matched with corresponding circular groove, an end that is help roll 66 penetrates the circular groove 64a on pushing out ring I 64, the other end penetrates the circular groove on pushing out ring II 68, adopt the mounting structure of circular groove, simple in structure, assembling easily, further makes the designs simplification of free wheel device, reduces costs,

Described pushing out ring I 64 and pushing out ring II 68 are all between 18He outer ring, outer ring 18, and the axial outside of pushing out ring I 64 and pushing out ring II 68 is respectively equipped with the radial bearing (figure is respectively radial bearing 67 and radial bearing 69) for 18He outer ring, outer ring 18 is rotatably assorted, the axial outside of pushing out ring I 64 and pushing out ring II 68 refers to vertically the direction to the free wheel device two ends; Adopt the radial bearing structure to form support to inner ring and the outer ring of free wheel device, certainly, this support should have certain radial clearance, to guarantee the normal engagement of free wheel device or disengaging engagement; Due to the support with radial bearing, can effectively prevent the reverse engagement of free wheel device, thereby guarantee the normal operation of free wheel device.

In the present embodiment, the diameter of described help roll 66 be less than rolling element diameter 1/2nd; Less help roll size can more be arranged rolling element, improves the operation stability of free wheel device and improves bearing capacity.

In the present embodiment, between described engagement space 63 wedge slots by the inner ring Excircle machining and inner ring cylindrical, form; Simplified processing process, improve work efficiency, and cut down finished cost; Those skilled in the art are according to the free wheel device principle, the wedge slot that forms the engagement space also can be arranged to outer ring, although processing mode is likely comparatively loaded down with trivial details, overall technical architecture can reach identical technique effect, belongs to the replacement that is equal to the technical program.

In the present embodiment, described rolling element 65 is roller; As shown in the figure, between help roll 66 and roller, be arranged in parallel, help roll 66 forms vertically line with roller and contacts, thereby help roll forms stable support to roller, avoids in prior art the unbalanced problem of roller support force.

In the present embodiment, described radial bearing (radial bearing 34 and radial bearing 36) is rolling bearing, pushing out ring I 64 and pushing out ring II 68 form respectively circumferentially inside axial ledge, this axial ledge is withstood the interior ring of corresponding rolling bearing vertically, be the interior ring that the axial ledge of pushing out ring I 64 is withstood radial bearing 34, the axial ledge of pushing out ring II 68 is withstood the interior ring of radial bearing 36; Both guarantee the smooth and easy operation of this free wheel device, can also guarantee its axially compact.

In the present embodiment, the diameter of described help roll 66 be less than rolling element diameter 1/3rd.

In the present embodiment, the one-body molded external gear that is provided with of described outer ring 18 cylindricals, be beneficial to transmission.

In the present embodiment, described speed change elastic element a7 and n shelves speed change elastic element (second gear speed change elastic element 47, three class gear shift elastic element 41 and four-speed gear shift elastic element 6) are speed change butterfly spring, speed change elastic element a7 is coated at pto＝power take-off 30, and second gear speed change elastic element 47, three class gear shift elastic element 41 and four-speed gear shift elastic element 6 are coated at corresponding second gear back shaft, third gear back shaft and fourth gear back shaft, speed change elastic element a7 and n shelves speed change elastic element (second gear speed change elastic element 47, three class gear shift elastic element 41 and four-speed gear shift elastic element 6) be respectively equipped with the pretightening force adjusting part, described pretightening force adjusting part comprises that axial limiting is installed on the adjustment disk of speed change butterfly spring end (adjustment disk 3 as shown in the figure, adjustment disk 72, adjustment disk 43 and adjustment disk 70), described adjustment disk (adjustment disk 3, adjustment disk 72, adjustment disk 43 and adjustment disk 70) be provided with the end cam groove, the end cam groove is by embedded adjustment pin (the corresponding adjustment pin 4 of adjustment disk 3, the corresponding adjustment pin 73 of adjustment disk 72, the corresponding adjustment pin 42 of adjustment disk 43 and the corresponding adjustment pin 71 of adjustment disk 70) push against speed change dish spring, speed change elastic element a7 is identical with the pretightening force adjusting part structure of n shelves speed change elastic element, at this, no longer repeats to set forth, when wearing and tearing occur in the mating face of the axial inner conical drogue 10 of cirque body and the axial external conical sleeve 14 of cirque body, can be by rotation adjustment disk 28, utilize the end cam groove to drive adjustment pin 26 to move to the direction of speed change butterfly spring and the axial external conical sleeve 14 of cirque body, as shown in the figure, be provided with annular bearing with rolling contact 29 between adjustment pin 26 and speed change butterfly spring, realize the invariable of pretightening force, to guarantee normally travelling of vehicle.

In the present embodiment, driving cam pair between the axial external conical sleeve a13 of described cirque body and pto＝power take-off 30 is the spiral prominence wheel set, as shown in the figure, the axial external conical sleeve a13 of cirque body inner circle is provided with spiral cam 13a, and pto＝power take-off 30 is provided with the spiral cam 15 be mated; The spiral prominence wheel set is the preferred structure of the present embodiment, also can adopt the secondary driving of existing other cam, such as end cam etc., but the spiral prominence wheel set can make this structure more compact, manufacture, install and keep in repair more convenient, and helix structure has unrivaled stability and smoothness, further increase work efficiency, have better energy conservation and consumption reduction effects, larger control vehicular discharge, be more suitable for the light roadsters such as two-wheel vehicle and use; The rotation direction of spiral cam is relevant with power output sense of rotation, those skilled in the art are according to above-mentioned record, under the prerequisite of learning transmission shaft power outbound course, can learn which kind of rotation direction of spiral cam can apply the axial thrust load of which kind of direction, does not repeat them here;

The shape line lift angle that forms whole end face impellers of the secondary group of cam a increases to 60 ° by 24 ° by conjuncted driven gear gradually to the axial external conical sleeve a13 of cirque body; The shape line lift angle that forms whole end face impellers of the secondary group of n shelves cam increases to 60 ° by 24 ° gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body; As shown in the figure, cam cover a and n shelves cam cover are three, the cam of take cover a is example, by conjuncted driven gear to the axial external conical sleeve a of cirque body, the end face impeller lift angle at first cam cover a23 two ends is respectively 24 ° and 36 °, and the end face impeller lift angle at second cam cover a21 two ends is respectively 36 ° and 48 °, and the end face impeller lift angle at the 3rd cam cover a19 two ends is respectively 48 ° and 60 °, n shelves cam cover is identical with it, does not repeat them here; The lift angle angular distribution is reasonable, is more conducive to realize the reasonable distribution between axial thrust load and circumference driving force, under the prerequisite of assurance saving driving source, realizes smooth-going gear shift.

In the present embodiment, the plane bearing that described speed change elastic element a7 and n shelves speed change elastic element all are coated at power input shaft by being slidably matched respectively and the plane bearing that is coated at n shelves back shaft that is slidably matched withstand the axial external conical sleeve a13 of cirque body and axial external conical sleeve one axial end portion of n shelves cirque body; Be relation one to one herein, do not repeat them here;

The diameter of described help roll 66 be less than rolling element diameter 1/2nd; Between described engagement space 63 wedge slots by the inner ring Excircle machining and inner ring cylindrical, form; Described

radial bearing

67,68 is rolling bearing, and pushing out ring I 64 and pushing out ring II 68 form respectively circumferentially inside axial ledge, and this axial ledge is withstood the interior ring of corresponding rolling bearing vertically;

Described n shelves free wheel device inner ring (second gear free wheel device inner ring 56, third gear free wheel device inner ring 34 and fourth gear free wheel device inner ring 20) is rotatably assorted and is coated at n shelves cam cover (second gear cam cover 53,54,57, third gear cam cover 36,35,32, fourth gear cam cover 14,17,22) cylindrical, the n shelves locking end face cam of the axial external conical sleeve of n shelves cirque body is positioned on the step of its outer surface formation, the axial inner conical drogue a16 of cirque body is rotatably assorted and is coated at cam cover a19, 21, 23 are provided with direct tube section, one grade of free wheel device outer ring 60 and (second gear free wheel device outer ring 55, n shelves free wheel device outer ring, third gear free wheel device outer ring 33 and fourth gear free wheel device outer ring 18) be external toothing, the direct tube section of the axial inner conical drogue a16 of described cirque body is provided with the first driving gear 74 with one grade of free wheel device outer ring 60 engagement driving, with (second gear free wheel device outer ring 55, n shelves free wheel device outer ring, third gear free wheel device outer ring 33 and fourth gear free wheel device outer ring 18) equal the second engaging gears 75 of engagement driving

In the present embodiment, as shown in the figure, described speed change elastic element a7 is arranged on the left side of the axial external conical sleeve a13 of cirque body, now, the expansion direction of the external spiral cam of the internal spiral cam of the axial external conical sleeve a13 of described cirque body and pto＝power take-off is identical with transmission shaft power output sense of rotation from left to right; Between the axial inner conical drogue a16 of power input shaft and cirque body, by gear frame, be in transmission connection, in the space of speed change elastic element a7 between gear frame and pto＝power take-off; Between the n shelves back shafts such as second gear back shaft, third gear back shaft and the axial external conical sleeve of n shelves cirque body, also by n shelves spiral prominence wheel set, coordinate, although, n shelves back shaft is follower structure, but this n shelves spiral prominence wheel set has played the effect that stops its resilience when the axial external conical sleeve of n shelves cirque body separates with the axial inner conical drogue a16 of cirque body, realize the locking that separates of clutch together with locking cam pair, n shelves end cam pair.

Above embodiment is optimum structure of the present invention, is not limiting the scope of the present invention; Such as, the Placements such as can adopting spline, flat key that is in transmission connection, be rotationally connected and generally can adopt bearing fit, just on Placement, adjust to some extent, etc. some technical characteristicss all can make corresponding change, and do not affect the realization of this goal of the invention.

The top gear power transmission line of the present embodiment:

The axial external conical sleeve a13 of the axial inner conical drogue a16 → cirque body of power input shaft 1 → cirque body → driving cam pair → pto＝power take-off 30 → output;

Now one grade of free wheel device and n shelves free wheel device inner ring surmount outer ring, and the resistance transfer route: the axial external conical sleeve a13 of pto＝power take-off 30 → driving cam pair → cirque body → compression speed change elastic element a7;

The axial external conical sleeve a13 of cirque body is applied to axial force and compress speed change elastic element (speed change butterfly spring) by the driving cam pair, when running resistance is increased to one regularly, this axial force is greater than the pretightening force of speed change dish spring setting and compresses speed change dish spring, the axial inner conical drogue a16 of cirque body is separated with the axial external conical sleeve a13 of cirque body, power is by following route transmission, i.e. fourth gear power transmission line:

The axial external conical sleeve a13 of the axial inner conical drogue a16 of the power input shaft 1 → cirque body → axial external conical sleeve 8 → fourth gear of fourth gear free wheel device outer ring 18 → fourth gear free wheel device inner ring, 20 → fourth gear cirque body axial inner conical drogue 10 → fourth gear cirque body cam pair → fourth gear driving gear 24 → conjuncted driven gear → cam secondary group a → cirque body → driving cam pair → pto＝power take-off 30 → outputting power; And now resistance acts on the driving cam pair all the time, and tractive force applies the axial force of compression speed change butterfly spring (speed change elastic element) by the secondary group of cam a, guarantees that the axial external conical sleeve a13 of cirque body separates with the axial inner conical drogue a16 of cirque body;

Simultaneously, fourth gear cam pair applies axial thrust load to fourth gear cam cover and the axial external conical sleeve of fourth gear cirque body, and when resistance increment, to setup parameter, the four-speed gear shift elastic element is compressed, and the axial external conical sleeve of fourth gear cirque body separates with the axial inner conical drogue of fourth gear cirque body; Power output is transmitted with the third gear route according to above-mentioned route transfer principle;

When transmission of power is transmitted by third gear output, tractive force is also by following route transmission: fourth gear free wheel device inner ring → fourth gear locking cam pair → axial external conical sleeve of fourth gear locking cam cover → fourth gear cirque body → compression speed change butterfly spring prevents in the third gear transmission process phenomenon that occurs that the axial inner conical drogue of fourth gear cirque body and the axial external conical sleeve of fourth gear cirque body are fitted; Now, third gear power also passes through following transfer route: third gear driven gear → conjuncted driven gear → fourth gear driving gear 24 → fourth gear cam pair → axial external conical sleeve 8 of fourth gear cirque body → compression four-speed gear shift elastic element; By the effect of fourth gear cam pair, fourth gear locking cam pair, while keeping the third gear transmission, the axial inner conical drogue 10 of fourth gear cirque body and the axial external conical sleeve 8 of fourth gear cirque body separates;

Third gear is to second gear to a grade, all identical with above-mentioned principle, does not repeat them here.

Above-mentioned transfer route can be found out, the present invention is when operation, the male cone (strobilus masculinus) of the inner conical surface of the axial inner conical drogue a16 of cirque body and the axial external conical sleeve a13 of cirque body fits tightly under the effect of speed change elastic element, form an automatic transmission that keeps certain pressure, and can adjust clutch by the adjustment adjustment disk and mesh required pressure, and compensate for wear, reach the transmission purpose; The direction that surmounts of free wheel device arranges according to transmission principle of the present invention and can realize, does not repeat them here.

Suppose that the pto＝power take-off outbound course is seen as counterclockwise from left to right, during motor vehicle starting, resistance is greater than driving force, resistance forces pto＝power take-off to clockwise rotate several angle, under the effect of driving cam pair, and the axial external conical sleeve a13 compression of cirque body speed change elastic element; The axial external conical sleeve a13 of cirque body separates with the axial inner conical drogue a16 of cirque body, synchronous, the engagement of fourth gear free wheel device, fourth gear output, resistance further strengthens, successively with third gear, second gear until one grade of transmission; Therefore, automatically realize the bottom gear starting, shortened the starting time, reduced starting force.Meanwhile, speed change elastic element a7 and n shelves speed change elastic element absorb movement resistor moment energy, for recovering gear transferring power soon, hold standby potential energy.

After starting successfully, running resistance reduces, when component is reduced to less than the pressure that speed change elastic element a7 and n shelves speed change elastic element produce, because passive movement resistance compression produces speed change elastic element a7 and n shelves speed change elastic element pressure discharges promotion from second gear, third gear, fourth gear, top gear rapidly successively, complete the male cone (strobilus masculinus) of the axial external conical sleeve a13 of cirque body and the inner conical surface of the axial inner conical drogue a16 of cirque body and recover to fit tightly state, other gear free wheel devicees are in surmounting state.

In running process, along with the variation self shifter principle of resistance to motion is the same, in the situation that do not need to cut off driving force, realize variable block, make whole locomotive operation steady, safe and low consumption, and transfer route simplification, improve transmission efficiency.

Finally explanation is, above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although with reference to preferred embodiment, the present invention is had been described in detail, those of ordinary skill in the art is to be understood that, can modify or be equal to replacement technological scheme of the present invention, and not breaking away from the spirit and scope of technical solution of the present invention, it all should be encompassed in the middle of claim scope of the present invention.

Claims

1. cam self-adapting multidrive more than a kind, comprise casing, power input shaft and pto＝power take-off, described power input shaft and pto＝power take-off are arranged at casing and are rotatably assorted with it, it is characterized in that: also comprise top gear assembly, one grade of assembly and output speed lower than the top gear assembly n shelves assembly higher than one grade of assembly, n shelves assembly is second gear, third gear ... with the n shelves;

2. many cam self-adaptings multidrive according to claim 1, it is characterized in that: n shelves free wheel device inner ring also coordinates with the axial external conical sleeve of n shelves cirque body by n shelves locking cam is secondary, and the axial external conical sleeve of n shelves cirque body and this n shelves locking cam pair are rotatably assorted at circumferencial direction; N shelves locking cam pair applies axial thrust load to the axial external conical sleeve of n shelves cirque body, this axial thrust load and n shelves speed change elastic element pretightening force opposite direction.

3. many cam self-adaptings multidrive according to claim 2, it is characterized in that: n shelves locking cam pair coordinates and forms by n shelves locking end face cam by between n shelves locking cam cover and n shelves free wheel device inner ring, axial contact and circumferencial direction is rotatably assorted between n shelves locking cam cover and the axial external conical sleeve of n shelves cirque body, the axial inner conical drogue of n shelves cirque body is provided with the axial inner conical drogue direct tube section of n shelves cirque body for coordinating with the transmission of n shelves free wheel device inner ring, described n shelves locking cam is placed in the axial inner conical drogue direct tube section of n shelves cirque body in overlapping and its cylindrical has annular spacing groove, at least one n shelves stop screw radially screws in the axial inner conical drogue direct tube section of n shelves cirque body and heads into annular spacing groove by the spacing ball of n shelves, the axial width of described annular spacing groove is greater than the spacing ball diameter of n shelves.

4. many cam self-adaptings multidrive according to claim 3, it is characterized in that: n shelves back shaft is respectively second gear back shaft, third gear back shaft and fourth gear back shaft, described one grade of transmission shaft, second gear back shaft, third gear back shaft and fourth gear back shaft are planetary structure and are centered around around pto＝power take-off, form five speed transmission, second gear mechanical intelligent adaptive rate assembly, third gear mechanical intelligent adaptive rate assembly and fourth gear mechanical intelligent adaptive rate assembly correspondence respectively are arranged at second gear back shaft, third gear back shaft and fourth gear back shaft, one grade of transmission shaft is by one grade of driving gear and be placed in one grade of gear engagement pair that the first speed driven gear of pto＝power take-off forms and output power to the secondary group of cam a, the secondary group of second gear cam outputs power to the secondary group of cam a by the second gear driving gear be placed on the second gear back shaft with the intermediate gear engagement pair that the second gear driven gear be placed on pto＝power take-off forms, the secondary group of third gear cam outputs power to the secondary group of cam a by the third speed drive gear be placed on the third gear back shaft with the three-range transmission engagement pair that the third gear driven gear be placed on pto＝power take-off forms, the secondary group of fourth gear cam outputs power to the secondary group of cam a by the fourth gear driving gear be placed on the fourth gear back shaft with the fourth gear engagement pair that the fourth gear driven gear be placed on pto＝power take-off forms, the velocity ratio of described one grade of gear engagement pair, intermediate gear engagement pair, three-range transmission engagement pair and fourth gear engagement pair reduces successively.

5. many cam self-adaptings multidrive according to claim 4, it is characterized in that: described first speed driven gear, the second gear driven gear, third gear driven gear and fourth gear driven gear are fixedly connected to form conjuncted driven gear, be placed in pto＝power take-off and be provided with at least two cam cover a, each cam cover a two ends is equipped with the end face impeller, between cam cover a, all by end face impeller engagement driving, form the secondary group of cam a between cam cover a and the axial external conical sleeve a of cirque body and between cam cover a and conjuncted driven gear, the shape line lift angle difference of the end face impeller at each cam cover a two ends, and the shape line lift angle of end face impeller that forms whole cams cover a of the secondary group of cam a is increased to the axial external conical sleeve a of cirque body gradually by conjuncted driven gear, be placed in n shelves back shaft and be provided with at least two n shelves cam covers, each n shelves cam cover two ends is equipped with the end face impeller, between n shelves cam cover, between n shelves cam cover and the axial external conical sleeve of n shelves cirque body and between n shelves cam cover and n shelves driving gear all by end face impeller engagement driving formation n shelves cam pair group, the shape line lift angle difference of the end face impeller at each n shelves cam cover two ends, and the end face impeller of whole n shelves cams covers of the secondary group of formation n shelves cam is increased gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body.

6. many cam self-adaptings multidrive according to claim 5, it is characterized in that: free wheel device includes outer ring, inner ring and rolling element, be formed for the engagement space of with rolling element, meshing or separating between described outer ring and inner ring, also comprise the help roll assembly, described help roll assembly at least comprises and is parallel to free wheel device axis the help roll spaced with rolling element, described help roll cylindrical contacts with adjacent rolling element cylindrical, and described help roll arranges in the movable mode of the circumferencial direction at free wheel device;

Described help roll assembly also comprises the help roll support, described help roll with can along the free wheel device circumferencial direction slide and the mode of rotating around self axis by the help roll stent support between outer ring and inner ring.

7. many cam self-adaptings multidrive according to claim 6, it is characterized in that: described help roll support comprises pushing out ring I and the pushing out ring II arranged corresponding to the help roll two ends, described pushing out ring I and pushing out ring II are respectively equipped with the circular groove along pushing out ring I and pushing out ring II circumferencial direction for penetrating for the help roll two ends, and described help roll two ends are slidably matched with corresponding circular groove; Described pushing out ring I and pushing out ring II are all between outer ring and inner ring, and the axial outside of pushing out ring I and pushing out ring II is respectively equipped with the radial bearing for outer ring and inner ring are rotatably assorted.

8. many cam self-adaptings multidrive according to claim 7 is characterized in that: described speed change elastic element a and n shelves speed change elastic element are speed change butterfly spring; Speed change elastic element a and n shelves speed change elastic element are respectively equipped with the pretightening force adjusting part, described pretightening force adjusting part comprises that axial limiting is installed on the adjustment disk of speed change butterfly spring end, described adjustment disk is provided with the end cam groove, and the end cam groove pushes against speed change dish spring by embedded adjustment pin.

9. many cam self-adaptings multidrive according to claim 8 is characterized in that: the driving cam between the axial external conical sleeve a of described cirque body and pto＝power take-off is secondary is the spiral prominence wheel set; The shape line lift angle that forms whole end face impellers of the secondary group of cam a increases to 60 ° by 24 ° by conjuncted driven gear gradually to the axial external conical sleeve a of cirque body; The shape line lift angle that forms whole end face impellers of the secondary group of n shelves cam increases to 60 ° by 24 ° gradually by n shelves driving gear to the axial external conical sleeve of n shelves cirque body.

10. many cam self-adaptings multidrive according to claim 9 is characterized in that: the plane bearing that described speed change elastic element a and n shelves speed change elastic element all are coated at power input shaft by being slidably matched respectively and the plane bearing that is coated at n shelves back shaft that is slidably matched withstand the axial external conical sleeve a of cirque body and axial external conical sleeve one axial end portion of n shelves cirque body;